CN1832880A - Telescopic shaft for motor vehicle steering - Google Patents
Telescopic shaft for motor vehicle steering Download PDFInfo
- Publication number
- CN1832880A CN1832880A CNA2004800225601A CN200480022560A CN1832880A CN 1832880 A CN1832880 A CN 1832880A CN A2004800225601 A CNA2004800225601 A CN A2004800225601A CN 200480022560 A CN200480022560 A CN 200480022560A CN 1832880 A CN1832880 A CN 1832880A
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- China
- Prior art keywords
- side contacts
- groove
- axle
- telescopic shaft
- female
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
- B62D—MOTOR VEHICLES; TRAILERS
- B62D1/00—Steering controls, i.e. means for initiating a change of direction of the vehicle
- B62D1/02—Steering controls, i.e. means for initiating a change of direction of the vehicle vehicle-mounted
- B62D1/16—Steering columns
- B62D1/18—Steering columns yieldable or adjustable, e.g. tiltable
- B62D1/185—Steering columns yieldable or adjustable, e.g. tiltable adjustable by axial displacement, e.g. telescopically
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/005—Guide rails or tracks for a linear bearing, i.e. adapted for movement of a carriage or bearing body there along
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/007—Hybrid linear bearings, i.e. including more than one bearing type, e.g. sliding contact bearings as well as rolling contact bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C29/00—Bearings for parts moving only linearly
- F16C29/12—Arrangements for adjusting play
- F16C29/123—Arrangements for adjusting play using elastic means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C3/00—Shafts; Axles; Cranks; Eccentrics
- F16C3/02—Shafts; Axles
- F16C3/03—Shafts; Axles telescopic
- F16C3/035—Shafts; Axles telescopic with built-in bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/06—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement
- F16D3/065—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow axial displacement by means of rolling elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
- F16D3/64—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members comprising elastic elements arranged between substantially-radial walls of both coupling parts
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2326/00—Articles relating to transporting
- F16C2326/20—Land vehicles
- F16C2326/24—Steering systems, e.g. steering rods or columns
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Ocean & Marine Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Steering Controls (AREA)
- Power Steering Mechanism (AREA)
- Support Of The Bearing (AREA)
- Springs (AREA)
- Bearings For Parts Moving Linearly (AREA)
Abstract
A telescopic shaft for a vehicle steering, assembled in a steering shaft of a vehicle and constructed by fitting a male shaft and a female shaft to each other so as to be unable to rotate but to be slidable, the telescopic shaft, has a first torque transferring member interposed via an elastic member between one line of axis-directional groove and one line of axis-directional groove formed respectively on an outer peripheral surface of the male shaft and on an inner peripheral surface of the female shaft; and a second torque transferring member interposed between another line of axis-directional groove and another line of axis-directional groove formed respectively along the outer peripheral surface of the male shaft and along the inner peripheral surface of the female shaft. The elastic member includes a transferring member sided contact portion abutting on the first torque transferring member, a groove sided contact portion spaced away at an predetermined interval substantially in a peripheral direction from the transferring member sided contact portion and abutting on a groove surface of the axis-directional groove of the male shaft or the female shaft; and a biasing portion elastically biasing the transferring member sided contact portion and the groove sided contact portion in such a direction as to separate from each other, wherein a rigidity of the transferring member sided contact portion is differentiated from a rigidity of the groove sided contact portion.
Description
Technical field
The present invention relates to be installed in the steering shaft of vehicle and by male axle and female axle being combined together so that it is rotatable the Vehicular turn that slidably constitutes with stretching (extending/collapsible) spool.
Background technology
The telescopic shaft of automobile steering mechanism device need have the longitudinal travel that produces when absorbing vehicle ' and prevent this displacement or transfer of vibration to the performance of steering handwheel.In addition, this telescopic shaft also needs to have the position of mobile steering handwheel vertically and adjusts the function of this position, so that obtain the optimum position of chaufeur steering vehicle.
Under any circumstance, telescopic shaft need reduce play (backlash) or click, reduce the play sensation of steering handwheel and the sliding resistance in the reduction slide process vertically.
In this case, traditional terms of settlement is, by with the male axle of nylon membrane parcel telescopic shaft and be coated with on slipper with grease and absorb or alleviate metallic noise, metal click etc., thereby reduces sliding resistance and play in rotational direction.
Yet, exist along with using nylon film wearing and tearing aggravation and play in rotational direction to become big situation.In addition, under the hi-heat situation in being exposed to engine room, the volume change of nylon film causes sliding resistance obviously to become big or wearing and tearing are significantly accelerated, and is big thereby play in rotational direction becomes.
In this case, according to disclosed telescopic shaft among Deutsche Reichspatent communique DE3730393C2, Japanese patent application laid-open communique No.2001-50293 and the Japanese patent application laid-open communique No.2001-193738, plant rolling body and be used for the male axle of precompressed and female precompressed elastic body between the inner peripheral surface of the outer peripheral face of male axle and female axle.By this structure, when sliding, elastic body is pressed against female axle etc. in advance with rolling body and goes up to can not producing the degree of play, thus can prevent male axle with female between play.In addition, when transmitting torque, elastic body can limit rolling body on circumferentially, and male axle and the female play that can prevent along its rotation direction.
Yet according to all these patent documentations, the raceway that is used for the elastic body of precompressed rolling body and the rolling body that reclines partly is made from a variety of materials, and takes different shapes owing to its purposes is different.
Its reason is that the raceway part of the rolling body that reclines must be born high pressure of contact surface.This means that torque must be via the rolling body transmission, the raceway of the rolling body that therefore requires to recline partly is hard rigid element.On the contrary, being used to produce the elastic body of biasing force need be by making such as the flexible material under the spring situation.
Can find out that from above-mentioned these aspects according to patent documentation, that is, Deutsche Reichspatent communique DE3730393C2, the raceway of the rolling body that reclines partly relate to use different material and different shapes, therefore, cause manufacturing cost to increase.
In addition, Deutsche Reichspatent communique DE3730393C2 for example understands an example of leaf spring, and wherein raceway partial sum elastic body is made by a kind of material.Yet this leaf spring connects via web, so structure becomes complicated, causes assembly cost to increase.In addition, as mentioned above, for by the rolling body transmitting torque, this leaf spring is at the pressure of contact surface that bears rolling body and provide in this use compatible aspect two of biasing force and have difficulty.
In addition, the open No.2001-193738 of Japanese patent application laid-open for example understands an example, and wherein elastic body and raceway part are integrally formed.Yet as above-mentioned situation, for by the rolling body transmitting torque, this leaf spring is at the pressure of contact surface that bears rolling body and provide in this use compatible aspect two of biasing force and have difficulty.
Summary of the invention
In view of the foregoing design the present invention, its objective is that providing a kind of can implement stable slip load and with the telescopic shaft for motor vehicle steering of high rigid state transmitting torque.
To achieve these goals, according to the present invention, provide in a kind of steering shaft that is installed in vehicle and by with male axle with female axle is combined together so that its rotatable telescopic shaft for motor vehicle steering that still slidably constitutes, described telescopic shaft comprises:
Be plugged on first torque transmission member between a row axial groove and the row axial groove that is formed on the described female inner peripheral surface on the outer peripheral face that is formed at described male axle via elastic body; And
Be plugged on second torque transmission member between another row axial groove on the inner peripheral surface that is formed at another row axial groove on the described male outer peripheral face and is formed at described female axle,
Described elastic body comprises:
The transferring elements side contacts portion of described first torque transmission member reclines;
Basic along circumferentially separating with predetermined space and the groove face side contacts portion of the groove face of the axial groove of recline described male axle or described female axle with described transferring elements side contacts portion; And
Along the bias voltage portion of described two contact parts of direction fexible bias pressure that described transferring elements side contacts portion and described groove face side contacts portion are separated from each other,
Wherein, the rigidity of described transferring elements side contacts portion is different with the rigidity of described groove face side contacts portion.
In addition, in the vehicle according to the invention steering telescopic shaft, preferably, described first torque transmission member is when described male axle and described female rolling body that rolls when moving axially relatively, and
Described second torque transmission member is when described male axle and described female slide mass that slides when moving axially relatively.
In addition, in the vehicle according to the invention steering telescopic shaft, described elastomeric described bias voltage portion can take crooked curved shape between described transferring elements side contacts portion and described groove face side contacts portion.
In addition, in the vehicle according to the invention steering telescopic shaft, described elastic body can constitute by the integrally formed product of being made by the thin plate springs steel.
In addition, in the vehicle according to the invention steering telescopic shaft, the superficial hardness of described transferring elements side contacts portion can be set at the superficial hardness height than the part that extends to described bias voltage portion from described groove face side contacts portion.
In addition, in the vehicle according to the invention steering telescopic shaft, described bias voltage portion can be formed with the hole that is used to reduce biasing force.
In addition, in the vehicle according to the invention steering telescopic shaft, the plate thickness of described transferring elements side contacts portion can be set at thicker than the plate thickness of the part that extends to described bias voltage portion from described groove face side contacts portion.
In addition, in the vehicle according to the invention steering telescopic shaft, described transferring elements side contacts portion can basically form and be dome-shaped.
Description of drawings
Fig. 1 is to use the lateral plan of the automobile steering mechanism device of telescopic shaft for motor vehicle steering according to an embodiment of the invention;
Fig. 2 is the longitudinal section according to the telescopic shaft for motor vehicle steering of the first embodiment of the present invention;
Fig. 3 is the cross sectional drawing along the line X-X among Fig. 2;
Fig. 4 A is the transparent view according to the leaf spring of first embodiment; Fig. 4 B is the transparent view according to the leaf spring of first variation of first embodiment; Fig. 4 C is the transparent view according to the leaf spring of second variation of first embodiment;
Fig. 5 is along the cross sectional drawing of the line X-X among Fig. 2, and telescopic shaft for motor vehicle steering according to a second embodiment of the present invention is shown;
Fig. 6 A is the transparent view according to the leaf spring of second embodiment; Fig. 6 B is the transparent view according to the leaf spring of first variation of second embodiment; Fig. 6 C is the transparent view according to the leaf spring of second variation of second embodiment;
Fig. 7 is the cross sectional drawing along the line X-X among Fig. 2, and the telescopic shaft for motor vehicle steering of a third embodiment in accordance with the invention is shown;
Fig. 8 A is the transparent view according to the leaf spring of the 3rd embodiment; Fig. 8 B is the transparent view according to the leaf spring of first variation of the 3rd embodiment; Fig. 8 C is the transparent view according to the leaf spring of second variation of the 3rd embodiment;
Fig. 9 is the cross sectional drawing along the line X-X among Fig. 2, and the telescopic shaft for motor vehicle steering of a fourth embodiment in accordance with the invention is shown;
Figure 10 A is the transparent view according to the leaf spring of the 4th embodiment; Figure 10 B is the transparent view according to the leaf spring of first variation of the 4th embodiment; Figure 10 C is the transparent view according to the leaf spring of second variation of the 4th embodiment.
The specific embodiment
Vehicular turn flexible (extending/collapsible) axle according to an embodiment of the invention is described with reference to the accompanying drawings.
(integral structure of vehicle steering shaft)
Fig. 1 is to use the lateral plan of the vehicle steering mechanism device of telescopic shaft for motor vehicle steering according to an embodiment of the invention.
With reference to Fig. 1, the steering hardware device is by constituting with the lower part: by upper bracket 101 and lower bracket 102 be installed on the vehicle body side part 100 and comprise steering column 103 and be diverted steering shaft 104 that tubing string 103 keeps rotationally on turn to axial region 120, be installed in the steering handwheel 105 of steering shaft 104 upper ends, be connected the following axial region 107 that turns to of the lower end of steering shaft 104 by universal-joint 106, be connected down the pinion shaft 109 that turns to axial region 107 by steering shaft joint 108, be connected the steering rack axle 112 on the pinion shaft 109 and be fixed on steering rack support unit 113 on another vehicle frame 110 of car body in the mode of supporting steering rack axle 112 by elastic body 111.
Turn to axial region 120 herein, and turn to axial region 107 to relate to down and use telescopic shaft for motor vehicle steering (hereinafter referred is " telescopic shaft ") according to an embodiment of the invention.Under turn to axial region 107 to constitute by hero axle being coupled to female axle, and thisly turn to axial region 107 need have the longitudinal travel that takes place when absorbing vehicle traveling process down and prevent this displacement or transfer of vibration performance to steering handwheel 105.Adopt the subframe structure at car body, make parts 100 that are used for fixing steering hardware top and the vehicle frame 110 that is used for fixing steering rack support unit 113 be provided with independently, and steering rack support unit 113 needs this performance by being fastened on such as elastic bodys such as rubber 111 under the situation on the vehicle frame 110.In addition, in another case, when the assembly crewman is assembled to steering shaft joint 108 on the pinion shaft 109, telescopic shaft is shortened, therefore need flexible (extending/collapsible) function so that make it to cooperate and be fixed on the pinion shaft 109.In addition, be arranged on steering hardware top on to turn to axial region 120 also be to constitute by hero axle being coupled to female axle, yet, turn to axial region 120 need have the position of mobile vertically steering handwheel 105 on this so that obtain the function that the optimum position of chaufeur steering vehicle is also adjusted this position subsequently, therefore require it to have the function of in axial direction extending and shrinking.Under above-mentioned all situations, all need telescopic shaft can reduce play noise, the play on the steering handwheel 105 sensation of auxiliary section and the sliding resistance in the sliding process vertically.
(first embodiment)
Fig. 2 is the longitudinal section according to the telescopic shaft for motor vehicle steering of the first embodiment of the present invention.
Fig. 3 is the cross sectional drawing along the line X-X among Fig. 2.
Fig. 4 A is the transparent view according to the leaf spring of first embodiment.Fig. 4 B is the transparent view according to the leaf spring of first variation of first embodiment.Fig. 4 C is the transparent view according to the leaf spring of second variation of first embodiment.
As shown in Figure 2, slidably male axle 1 and female axle 2 do not constitute telescopic shaft for motor vehicle steering (will abbreviate telescopic shaft as hereinafter) so that it is rotatable by being combined together.
As shown in Figure 3, the mode of extending with the outer peripheral face along hero axle 1 is formed on the three row axial grooves 3 that week upwards is provided with 120 equal intervals of spending (position phase).Corresponding with these grooves, the mode of extending with the inner peripheral surface along female axle 2 is formed on the three row axial grooves 5 that week upwards is provided with 120 equal intervals of spending (position phase).
Between the axial groove 5 of male 1 axial groove 3 and female axle 2, rollably be plugged with a plurality of rolling bodys or the ball that are defined as rigidity globoid 7 that when two axles 1,2 move axially relatively, roll.The cross section of the axial groove 5 of female axle 2 is circular shape or cusped arch shape.
The axial groove 3 of male axle 1 constitutes the bottom surface 3b between the flattened side 3a by being shown to be line symmetry and a pair of flattened side 3a of bevelled and to be formed flatly at this about diameter.
Thereby between male 1 axial groove 3 and globoid 7, be plugged with the globoid 7 that reclines and apply the leaf spring 9 of precompressed to it.
The 9c of bias voltage portion has the basic shape of U-shaped that is, wherein its bottom is substantially with the circular shape bending.But have this 9c of bias voltage portion fexible bias pressure globoid side contacts 9a of portion of curved shape and the groove face side contacts 9b of portion so that it is separated from each other.
Therefore, according to first embodiment, leaf spring 9 has the contact part 9a of the globoid 7 that reclines integratedly and produces the 9c of bias voltage portion of precompressed, therefore controls precompressed so that the pressure of contact surface of contact part 9a on globoid 7 can be too high very unimportant.Therefore, according to first embodiment, leaf spring 9 is set to has such structure, the precompressed (that is, when making male axle 1 load that the bias voltage 9c of portion produces when the inboard of female axle 2 relatively rotates) that described structure makes the 9c of bias voltage portion produce can not surpass the allowed value of the surface pressure that contact part 9a produces on globoid 7.
As shown in Figure 3, be formed on the three row axial grooves 4 that week upwards is provided with 120 equal intervals of spending (position phase) in the mode of on the outer peripheral face of male axle 1, extending.Corresponding with these grooves, be formed on the three row axial grooves 6 that week upwards is provided with 120 equal intervals of spending (position phase) in the mode of on the inner peripheral surface of female axle 2, extending.
Between the axial groove 6 of male 1 axial groove 4 and corresponding with it female axle 2, be plugged with the column 8 (being also referred to as slide mass or needle roller in this manual) of a plurality of rigid bodies that when two axles 1,2 move axially relatively, slide in mode with minim gap.The cross section of each all is circular shape or cusped arch shape in these axial grooves 4,6.
As shown in Figure 2, the end of male axle 1 is formed with minor diameter part 1a.This minor diameter part 1a has the axially movable check plate 10 that is used to control needle roller 8.Check plate 10 is by the axial precompressed elastic body 11 that comprises disk spring and be used for the pair of plates 12,13 that this axial precompressed elastic body 11 remains between them is constituted.
In first embodiment, check plate 10 with dull and stereotyped 13, axially precompressed elastic body 11 and dull and stereotyped 12 is engaged in mode on the minor diameter part 1a in this order by being firmly fixed at minor diameter part 1a by riveted joint or the plastic deformation that clenches.By this way, check plate 10 in axial direction is fixed.The fixing means that should be noted that check plate 10 is not limited to by by riveted joint or the plastic deformation that clenches, but also can relate to the device of use such as locating ring, screw connection and pushing nut (push nut).In addition, check plate 10 formations can be so that flat board 13 is resisted against the mode precompressed needle roller 8 on the needle roller 8 so that it can be mobile vertically owing to axial precompressed elastic body 11 (disk spring).
In addition, according to first embodiment, each all substantially for circular shape and form with male axle 1 outer peripheral face on six coaxial in the axial direction juts 14 of six row axial grooves 3,4, be engaged in the mode that has the gap diametrically in female 2 the six row axial grooves 5,6.
Therefore; if globoid 7 or column 8 come off or because any former thereby cause damaging from male axle 1; the jut 14 of male axle 1 is engaged in the axial groove 5,6 of female axle 2, but therefore male axle 1 and female axle 2 transmitting torques and can play the effect of failure protection function.
In addition, in this case, owing to have the gap between axial groove 5,6 and jut 14, so chaufeur can feel bigger play by steering handwheel, thereby perceives fault in the steering swivel system etc.
And; jut 14 aligns with globoid 7 and column 8 in the axial direction; therefore play effect, thereby reduce the possibility that globoid 7 and column 8 come off and can further improve failure protection function as the axially movable hill holder that is used to regulate globoid 7 and column 8.
And jut 14 aligns with globoid 7 and column 8 in the axial direction, therefore can obtain compact design by the radial dimension that reduces male axle 1 and female axle 2.
And, can between axial groove 5, leaf spring 9 and the globoid 7 of the axial groove 3 of male axle 1, female axle 2, apply lubricant.In addition, also can between the axial groove 6 of axial groove 4, column 8 and the female axle 2 of male axle 1, apply lubricant.
In the telescopic shaft of constructing like this, globoid 7 is plugged between male axle 1 and the female axle 2, and leaf spring 9 is pressed against on the female axle 2 globoid 7 in advance to the degree that does not have the play generation.Therefore, when transmitting torque not, can guarantee to prevent the play between male axle 1 and the female axle 2, and Damxung axle 1 and female axle 2 be when moving axially relatively, can be under stable slip load mobile and can not produce any play.
When transmitting torque, leaf spring 9 elastic deformations and on circumferentially restriction globoid 7, and be plugged on the effects of three row columns, the 8 main execution transmitting torques between male axle 1 and the female axle 2.
For example, under the situation of male axle 1 input torque, in the early stage the stage, because the precompressed of leaf spring 9, so there is not play, leaf spring 9 produces the antagonistic force of opposing torque, thus transmitting torque.The whole torques of transmission under the state that the torque of torque transmitted between male axle 1, leaf spring 9, globoid 7 and the female axle 2 and input balances each other.
When torque further increases, disappear by in rotational direction gap between the male axle 1 of column 8, the female axle 2, column 8 transmits the increase part of torques after this by male axle 1 and female axle 2.Therefore, can prevent play in rotational direction between male axle 1 and the female axle 2 reliably, and under the state of high rigidity transmitting torque.
From described structure up to the present, according to first embodiment, owing to also be provided with column 8 except globoid 7, therefore when very big torque input, most of load can both be born by column 8.Therefore, axial groove 5 that can be by reducing female axle 2 and the contact pressure between the globoid 7 improve durability, simultaneously, when torque load is very big, can be under the state of high rigidity transmitting torque.
In addition, owing to column 8 and male axle 1 and female axle 2 recline, thus can reduce to act on the moment of torsion on the globoid 7, and the lateral slip of inhibition leaf spring 9, therefore, it is excessive to prevent to lag behind.
Therefore,, can realize stable slip load according to first embodiment, and can by prevent reliably in rotational direction play and under the state of high rigidity transmitting torque.
Should be noted that globoid 7 is preferably the ball of rigid body.Also preferably, the column 8 of rigid body is preferably needle roller.
Because column (needle roller hereinafter referred to as) 8 bears load with line contact, thus with compare to contact the ball that bears load, can obtain such as contact pressure being suppressed to be lower many advantages.Therefore, compare with the situation of all row being arranged to the ball rolling structure, this setting has following advantage.
Compare with the ball rolling structure, the attenuating of slipper is bigger.Therefore, vibration absorption is good.
Because needle roller and male axle and little contact of female axle, thus the fluctuating range of the load that slides can be suppressed for lower, and because the vibration that this fluctuation causes can not pass to steering swivel system.
When transmitting identical torque, in the needle roller structure, contact pressure can be suppressed for lower, therefore, can by shortening vertically length and usage space effectively.
When transmitting identical torque, in the needle roller structure, contact pressure can be suppressed for lower, so do not need to make the female skin-hard additional process of axial groove by heat treatment etc.
Can reduce the number of components.
Can improve assembly performance.
Can reduce assembly cost.
As mentioned above, needle roller plays important effect during transmitting torque between male axle 1 and female axle 2, and with female 2 inner peripheral surface moving contact.This needle roller structure is compared with the spline fitted structure of routine and is had the following advantages.
Needle roller is for producing goods in enormous quantities, so manufacturing cost is very low.
Because needle roller grinds after heat treatment, thus the superficial hardness height, and excelling in abrasion resistance.
Because needle roller grinds,, therefore, the load that slides can be suppressed for lower so they have meticulous roughness of surface and low coefficient of sliding resistance.
Therefore can change the length or the layout of needle roller according to usage condition, can change design philosophy and needle roller is used for various application.
According to usage condition, also need further to reduce coefficient of sliding resistance sometimes.Therefore in this case, only needle roller is carried out surface treatment and just can change its sliding properties, can change design philosophy and needle roller is used for various application.
Therefore the needle roller that can have the various outer diameter of several microns difference with the low cost manufacturing can reduce to minimum with between male axle and the needle roller and the gap between needle roller and the female axle by selecting the needle roller diameter.Therefore can easily improve the rigidity of the torsional direction of axle.
In addition, each leaf spring 9 comprises in its left and right sides respectively: at a pair of globoid side contacts 9a of portion of 2 globoids 7 of locating to recline; Basic edge circumferentially and the globoid side contacts 9a of portion separates with predetermined space and a pair of groove face side contacts 9b of portion of the flattened side 3a of the axial groove 3 of the male axle 1 that reclines; Be used for along a pair of bias voltage 9c of portion of the direction fexible bias pressure 9a of portion, 9b that globoid side contacts 9a of portion and the groove face side contacts 9b of portion are separated from each other; And a pair of bottom 9d relative with the bottom surface 3b of axial groove 3.
The 9c of bias voltage portion has the basic shape of U-shaped that is, wherein its bottom is substantially with the circular shape bending.But have this 9c of bias voltage portion fexible bias pressure globoid side contacts 9a of portion of curved shape and the groove face side contacts 9b of portion so that it is separated from each other.Therefore, its globoid side contacts 9a of portion can guarantee sufficient deflection by the become leaf spring 9 of abundant deflection of the 9b of bias voltage portion.
According to first embodiment, as shown in Fig. 3 and 4A, the globoid side contacts 9a of portion of leaf spring of globoid 7 of reclining has high surface hardness (expectation is equal to or higher than HRC40), and other parts (that is, the 9b of groove face side contacts portion, the 9c of bias voltage portion and bottom 9d) are set to and have low superficial hardness (expectation is equal to or less than HRC30).Should be noted that in Fig. 4 A the globoid side contacts 9a of portion with high surface hardness extends and symmetrical a pair of flat rectangular part vertically.
By this structure, the globoid side contacts 9a of portion of the globoid 7 that reclines is rigidity, therefore can fully bear the stress at the contact point place that contacts with globoid 7.
On the contrary, the part with low superficial hardness is easy to limpen when bearing displacement, thereby can prevent at the stress at the contact point place that contacts with globoid 7 excessive.
That is, between the precompressed that the purpose that difference is provided aspect the hardness (rigidity) is to take place at the surface pressure (stress) and the bias voltage portion 9c place at contact point place, average out.If use the plate thickness of conventional integrally formed product and leaf spring even, the balance that obtains between them is very difficult.Should be noted that hereinafter and will illustrate that present embodiment is the structure of inventing in order to obtain this balance fully.
In first embodiment, in order to obtain the precompressed balance of leaf spring 9, the rigidity of the globoid side contacts 9a of portion of leaf spring 9 is set to the rigidity that is higher than the groove face side contacts 9b of portion.
Can find out that from foregoing according to first embodiment, leaf spring 9 has the space between the groove face side contacts 9b of portion of the globoid side contacts 9a of portion of the globoid 7 that reclines and the axial groove 3 that reclines, and between them, set up the elasticity connection.By this design, when setting, can reduce, and, can in the long term, obtain the precompressed performance of expection by preventing permanent strain owing to the leaf spring 9 that permanent deformation caused at the stress of leaf spring 9 with the contact part place of globoid 7.
In addition, leaf spring 9 can be guaranteed sufficient deflection, and on globoid 7 and leaf spring 9, can not apply excessive load (stress), therefore, when transmitting torque, can reduce the stress at the contact point place between globoid 7 and leaf spring 9, thereby can keep the precompressed performance and can not cause heavily stressed by preventing [permanent strain] that permanent deformation from causing.
And, to be done to such an extent that rigidity is big with the contact point of globoid 7, the part with spring performance is set to such an extent that be easy to bending, thereby can make single parts have raceway face and spring performance simultaneously.In addition, the structure among first embodiment is such, that is, therefore column 8 main transmitting torques more excessive stress can not occur between male axle 1, female axle 2, leaf spring 9 and globoid 7.
Therefore, by avoiding the permanent strain that excessive stresses prevents leaf spring 9 on leaf spring 9, occurring, can in the long term, keep the precompressed performance of expection thus.In addition, do not need strict controlling dimension precision, and can make leaf spring 9 and raceway part, thereby the mode that can help to assemble reduces manufacturing cost by a kind of material.
Next, Fig. 4 B is the transparent view according to the leaf spring of first variation of first embodiment.
According to first variation, the 9c of bias voltage portion that is defined as the crimping portion of leaf spring 9 is formed with a plurality of holes 21, and aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.
According to this layout, can not apply excessive stress at contact point place with globoid 7.That is, when applying torque load, globoid 7 in rotational direction relatively moves, yet, at this moment, be set to such an extent that be easy to bending as the 9c of bias voltage portion of crimping portion, therefore can not apply excessive stress at contact point place with globoid 7.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Next, Fig. 4 C is the transparent view according to the leaf spring of second variation of first embodiment.
The crooked R portion that is formed at the root place of the leaf spring 9 between globoid side contacts 9a of portion and the bottom surface 9d is formed with a plurality of holes 22, and aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.
According to this design, can not apply excessive stress at contact point place with globoid 7.Promptly, before applying torque load (precompressed that produce owing to assembling this moment causes producing stress at the contact point place of leaf spring 9), be easy to bending owing to form porose 22 part in the crooked R of leaf spring 9 one, therefore the contact point place at leaf spring 9 and globoid 7 can not apply excessive stress when assembling.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
(second embodiment)
Fig. 5 is along the cross sectional drawing of the line X-X among Fig. 2, and telescopic shaft for motor vehicle steering according to a second embodiment of the present invention is shown.
Fig. 6 A is the transparent view according to the leaf spring of second embodiment.Fig. 6 B is the transparent view according to the leaf spring of first variation of second embodiment.Fig. 6 C is the transparent view according to the leaf spring of second variation of second embodiment.
As shown in Fig. 5 and Fig. 6 A, according to second embodiment, to compare with first embodiment, the plate thickness of the globoid side contacts 9a of portion of the globoid 7 that reclines is set to thicker than the plate thickness of the part that extends to the 9c of bias voltage portion from the groove face side contacts 9b of portion.Therefore, according to second embodiment, with by obtaining above-mentioned precompressed balance providing the mode that difference makes the rigidity of these two parts 9a and 9b differ from one another aspect the globoid side contacts 9a of portion of leaf spring 9 and the plate thickness between the groove face side contacts 9b of portion.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Can find out that from foregoing according to second embodiment, leaf spring 9 can be guaranteed sufficient deflection, on globoid 7 and leaf spring 9, can not apply excessive load (stress), and, when transmitting torque, can reduce the stress at the place, contact site between globoid 7 and leaf spring 9.By this design, can not produce heavily stressed, and can in the long term, keep the precompressed performance by preventing [permanent strain] that permanent deformation causes.
And, to be done to such an extent that rigidity is big with the contact point of globoid 7, the part with spring performance is set to such an extent that be easy to bending, thereby can make single parts have raceway face and spring performance simultaneously.
Therefore, by avoiding the permanent strain that excessive stresses prevents leaf spring 9 on leaf spring 9, occurring, can in the long term, keep the precompressed performance of expection thus.In addition, do not need strict controlling dimension precision, and can make leaf spring 9 and raceway part, thereby the mode that can help to assemble reduces manufacturing cost by a kind of material.
Next, Fig. 6 B is the transparent view according to the leaf spring of first variation of second embodiment.According to first variation, all be formed with a plurality of holes 21 as the crimping portion of the 9c of bias voltage portion of leaf spring 9, aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.According to this layout, can not apply excessive stress at contact point place with globoid 7.That is, when applying torque load, globoid 7 in rotational direction relatively moves, yet at this moment, bias voltage portion 9c (crimping portion) is set to such an extent that be easy to bending, therefore can not apply excessive stress at the contact point place with globoid 7.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Next, Fig. 6 C is the transparent view according to the leaf spring of second variation of second embodiment.The crooked R portion that is formed at the root place of the leaf spring 9 between globoid side contacts 9a of portion and the bottom surface 9d is formed with a plurality of holes 22, and aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.According to this design, can not apply excessive stress at contact point place with globoid 7.Promptly, before applying torque load (precompressed that produce owing to assembling this moment causes producing stress at the contact point place of leaf spring 9), be easy to bending owing to form porose 22 part in the crooked R of leaf spring 9 one, therefore the contact point place at leaf spring 9 and globoid 7 can not apply excessive stress when assembling.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
(the 3rd embodiment)
Fig. 7 is the cross sectional drawing along the line X-X among Fig. 2, and the telescopic shaft for motor vehicle steering of a third embodiment in accordance with the invention is shown.
Fig. 8 A is the transparent view according to the leaf spring of the 3rd embodiment.Fig. 8 B is the transparent view according to the leaf spring of first variation of the 3rd embodiment.Fig. 8 C is the transparent view according to the leaf spring of second variation of the 3rd embodiment.
As shown in Fig. 7 and Fig. 8, according to the 3rd embodiment, compare with first embodiment, the globoid side contacts 9a of portion of the globoid 7 that reclines basically forms and is circular shape.By this structure, can make pressure of contact surface be lower than the pressure of contact surface in the aspect.According to the 3rd embodiment, the globoid side contacts 9a of portion of the globoid 7 that reclines basically forms and is circular shape, therefore is set to be higher than be the groove face side contacts 9b of portion of aspect substantially.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Can find out that from foregoing according to the 3rd embodiment, leaf spring 9 can be guaranteed sufficient deflection, on globoid 7 and leaf spring 9, can not apply excessive load (stress), and, when transmitting torque, can reduce the stress at the place, contact site between globoid 7 and leaf spring 9.By this design, can not produce heavily stressed, and can in the long term, keep the precompressed performance by preventing [permanent strain] that permanent deformation causes.
And, to be done to such an extent that rigidity is big with the contact point of globoid 7, the part with spring performance is set to such an extent that be easy to bending, thereby can make single parts have raceway face and spring performance simultaneously.
Therefore, by avoiding the permanent strain that excessive stresses prevents leaf spring 9 on leaf spring 9, occurring, can in the long term, keep the precompressed performance of expection thus.In addition, do not need strict controlling dimension precision, and can make leaf spring 9 and raceway part, thereby the mode that can help to assemble reduces manufacturing cost by a kind of material.
Next, Fig. 8 B is the transparent view according to the leaf spring of first variation of the 3rd embodiment.According to first variation, all be formed with a plurality of holes 21 as the crimping portion of the 9c of bias voltage portion of leaf spring 9, aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.According to this layout, can not apply excessive stress at contact point place with globoid 7.That is, when applying torque load, globoid 7 in rotational direction relatively moves, yet at this moment, bias voltage portion 9c (crimping portion) is set to such an extent that be easy to bending, therefore can not apply excessive stress at the contact point place with globoid 7.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Next, Fig. 8 C is the transparent view according to the leaf spring of second variation of the 3rd embodiment.The crooked R portion that is formed at the root place of the leaf spring 9 between globoid side contacts 9a of portion and the bottom surface 9d is formed with a plurality of holes 22, and aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.According to this design, can not apply excessive stress at contact point place with globoid 7.Promptly, before applying torque load (precompressed that produce owing to assembling this moment causes producing stress at the contact point place of leaf spring 9), be easy to bending owing to form porose 22 part in the crooked R of leaf spring 9 one, therefore the contact point place at leaf spring 9 and globoid 7 can not apply excessive stress when assembling.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
(the 4th embodiment)
Fig. 9 is the cross sectional drawing along the line X-X among Fig. 2, and the telescopic shaft for motor vehicle steering of a fourth embodiment in accordance with the invention is shown.
Figure 10 A is the transparent view according to the leaf spring of the 4th embodiment.Figure 10 B is the transparent view according to the leaf spring of first variation of the 4th embodiment.Figure 10 C is the transparent view according to the leaf spring of second variation of the 4th embodiment.
As shown in Fig. 9 and Figure 10 A, according to the 4th embodiment, compare with first embodiment, the plate thickness of the globoid side contacts 9a of portion of globoid 7 of reclining is set to thicker than the plate thickness of the part that extends to the 9c of bias voltage portion from the groove face side contacts 9b of portion, and the surface of the globoid 7 that reclines basically forms and is circular shape.By this layout, can make pressure of contact surface with globoid 7 be lower than the pressure of contact surface in the aspect.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Can find out that from foregoing according to the 4th embodiment, leaf spring 9 can be guaranteed sufficient deflection, on globoid 7 and leaf spring 9, can not apply excessive load (stress), and, when transmitting torque, can reduce the stress at the place, contact site between globoid 7 and leaf spring 9.By this design, can not produce heavily stressed, and can in the long term, keep the precompressed performance by preventing [permanent strain] that permanent deformation causes.
And, to be done to such an extent that rigidity is big with the contact point of globoid 7, the part with spring performance is set to such an extent that be easy to bending, thereby can make single parts have raceway face and spring performance simultaneously.
Therefore, by avoiding the permanent strain that excessive stresses prevents leaf spring 9 on leaf spring 9, occurring, can in the long term, keep the precompressed performance of expection thus.In addition, do not need strict controlling dimension precision, and can make leaf spring 9 and raceway part, thereby the mode that can help to assemble reduces manufacturing cost by a kind of material.
Next, Figure 10 B is the transparent view according to the leaf spring of first variation of the 4th embodiment.According to first variation, all be formed with a plurality of holes 21 as the crimping portion of the 9c of bias voltage portion of leaf spring 9, aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.According to this layout, can not apply excessive stress at contact point place with globoid 7.That is, when applying torque load, globoid 7 in rotational direction relatively moves, yet at this moment, the 9c of bias voltage portion is set to such an extent that be easy to bending, therefore can not apply excessive stress at the contact point place with globoid 7.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Next, Figure 10 C is the transparent view according to the leaf spring of second variation of the 4th embodiment.The crooked R portion that is formed at the root place of the leaf spring 9 between globoid side contacts 9a of portion and the bottom surface 9d is formed with a plurality of holes 22, and aliging in the axial direction in described hole, is used to reduce biasing force, thereby make leaf spring 9 be easy to bending.According to this design, can not apply excessive stress at contact point place with globoid 7.Promptly, before applying torque load (precompressed that produce owing to assembling this moment causes producing stress at the contact point place of leaf spring 9), be easy to bending owing to form porose 22 part in the crooked R of leaf spring 9 one, therefore the contact point place at leaf spring 9 and globoid 7 can not apply excessive stress when assembling.Even should be noted that at superficial hardness and also can as among first embodiment, partly change superficial hardness under the situation uniformly generally.
Should be noted that the present invention is not limited to the foregoing description, but can have multiple modification.
As mentioned above, each elastic body all has the space between the groove face side contacts portion of the transferring elements side contacts portion of first torque transmission member that reclines and the axial groove that reclines, and sets up the elasticity connection between them.By this design, when setting, can reduce the stress at the contact part place between first torque transmission member and elastic body, and by preventing can in the long term, to obtain the precompressed performance of expection owing to the elastomeric permanent strain that permanent deformation caused.
In addition, elastic body can be guaranteed sufficient deflection, and on first torque transmission member and elastic body, can not apply excessive load (stress), therefore, when transmitting torque, can reduce the stress at the contact point place between first torque transmission member and elastic body, thereby can in the long term, keep the precompressed performance and can not cause heavily stressed by preventing [permanent strain] that permanent deformation from causing.
And, to be done to such an extent that rigidity is big with the contact point of first torque transmission member, the part with spring performance is set to such an extent that be easy to bending, thereby can make single parts have raceway face and spring performance simultaneously.In addition, the structure among the 4th embodiment is such, that is, therefore the main transmitting torque of second torque transmission member more excessive stress can not occur between male axle, female axle, elastic body and first torque transmission member.
Therefore, prevent elastomeric permanent strain, can in the long term, keep the precompressed performance of expection thus by avoiding excessive stress on elastic body, occurring.In addition, do not need strict controlling dimension precision, and can make elastic body and raceway part, thereby the mode that can help to assemble reduces manufacturing cost by a kind of material.
Claims (11)
1. in the steering shaft that is installed in vehicle and by with male axle with female axle is combined together so that its rotatable telescopic shaft for motor vehicle steering that still slidably constitutes, described telescopic shaft comprises:
Be plugged on first torque transmission member between a row axial groove and the row axial groove that is formed on the described female inner peripheral surface on the outer peripheral face that is formed at described male axle via elastic body; And
Be plugged on second torque transmission member between another row axial groove on the inner peripheral surface that is formed at another row axial groove on the described male outer peripheral face and is formed at described female axle,
Described elastic body comprises:
The transferring elements side contacts portion of described first torque transmission member reclines;
Basic along circumferentially separating with predetermined space and the groove face side contacts portion of the groove face of the axial groove of recline described male axle or described female axle with described transferring elements side contacts portion; And
Along the bias voltage portion of described two contact parts of direction fexible bias pressure that described transferring elements side contacts portion and described groove face side contacts portion are separated from each other,
Wherein, the rigidity of described transferring elements side contacts portion is different with the rigidity of described groove face side contacts portion.
2. telescopic shaft for motor vehicle steering according to claim 1 is characterized in that, described first torque transmission member is when described male axle and described female rolling body that rolls when moving axially relatively, and
Described second torque transmission member is when described male axle and described female slide mass that slides when moving axially relatively.
3. telescopic shaft for motor vehicle steering according to claim 1 and 2 is characterized in that, described elastomeric described bias voltage portion takes crooked curved shape between described transferring elements side contacts portion and described groove face side contacts portion.
4. telescopic shaft for motor vehicle steering according to claim 1 and 2 is characterized in that, described elastic body constitutes by the integrally formed product of being made by the thin plate springs steel.
5. telescopic shaft for motor vehicle steering according to claim 1 and 2 is characterized in that, the superficial hardness of described transferring elements side contacts portion is set at the superficial hardness height than the part that extends to described bias voltage portion from described groove face side contacts portion.
6. telescopic shaft for motor vehicle steering according to claim 1 and 2 is characterized in that, described bias voltage portion is formed with the hole that is used to reduce biasing force.
7. telescopic shaft for motor vehicle steering according to claim 1 and 2 is characterized in that, the plate thickness of described transferring elements side contacts portion is set at thicker than the plate thickness of the part that extends to described bias voltage portion from described groove face side contacts portion.
8. telescopic shaft for motor vehicle steering according to claim 1 and 2 is characterized in that, described transferring elements side contacts portion basically forms and is dome-shaped.
9. telescopic shaft for motor vehicle steering comprises:
Be formed with the male axle of first and second axial grooves that on outer peripheral face, extend vertically at interval at a predetermined angle;
With the female axle of the coaxial setting of described male axle, described female axle be formed with the corresponding mode of described first and second axial grooves in the inner peripheral surface upper edge axially extended third and fourth axial groove, and be embedded in outward on the described male axle;
Be plugged on described first axial groove of described male axle and first torque transmission member of described third axle between groove of described female axle;
Be plugged on the elastic body that also extends vertically between described first axial groove of described first torque transmission member and described male axle;
Second torque transmission member between described second axial groove that is plugged on described male axle and the described female described four-axial groove,
Wherein, but described telescopic shaft is installed in the steering shaft of vehicle and by described male axle and described female are combined together so that it can not relatively rotate slidably constitutes,
Described elastic body has formed first contact part, second contact part and bias voltage portion, at the described first contact part place, described elastic body contacts with described first torque transmission member, at the described second contact part place, described elastic body contacts with the described groove face of described male axle, and described bias voltage portion connects first and second contact parts and first and second contact parts are flexibly remained and is separated from each other so that described parts are under precompressed and the contact condition; And
The precompressed that is produced by described bias voltage portion is set to be no more than the allowed value that described second contact part is resisted the surface pressure of described first torque transmission member.
10. telescopic shaft for motor vehicle steering according to claim 10 is characterized in that, described first axial groove of described male axle has about the groove side of diametric(al) line symmetry and the groove bottom that connects described groove side,
Described elastomeric described first contact part is that the transferring elements side contacts portion by described first transferring elements that all reclines constitutes,
Described elastomeric described second contact part is that the groove face side contacts portion by the described groove side that all reclines constitutes,
Described bias voltage portion is connected described transferring elements side contacts portion and along these two contact parts of direction bias voltage that described two contact parts are separated from each other at outside diameter with described groove face side contacts portion, and
Described elastic body also has the connecting portion that described transferring elements side contacts portion is connected with described groove face side contacts portion at internal side diameter integratedly.
11., it is characterized in that described first torque transmission member is made of a plurality of spherical rolling bodys according to claim 10 or 11 described telescopic shaft for motor vehicle steering, and
Described second torque transmission member is made of needle roller.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003190514 | 2003-07-02 | ||
| JP190514/2003 | 2003-07-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1832880A true CN1832880A (en) | 2006-09-13 |
| CN100436226C CN100436226C (en) | 2008-11-26 |
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ID=33562335
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800225601A Expired - Fee Related CN100436226C (en) | 2003-07-02 | 2004-06-11 | Telescopic shaft for motor vehicle steering |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US7404768B2 (en) |
| EP (1) | EP1652748A4 (en) |
| JP (1) | JPWO2005002947A1 (en) |
| CN (1) | CN100436226C (en) |
| WO (1) | WO2005002947A1 (en) |
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| CN110877634A (en) * | 2019-12-23 | 2020-03-13 | 天津市精一紧固件有限公司 | Steering shaft of motor vehicle |
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| JP4770193B2 (en) * | 2005-02-16 | 2011-09-14 | 日本精工株式会社 | Telescopic shaft for vehicle steering |
-
2004
- 2004-06-11 JP JP2005511316A patent/JPWO2005002947A1/en active Pending
- 2004-06-11 EP EP04746089A patent/EP1652748A4/en not_active Withdrawn
- 2004-06-11 US US10/563,324 patent/US7404768B2/en not_active Expired - Lifetime
- 2004-06-11 CN CNB2004800225601A patent/CN100436226C/en not_active Expired - Fee Related
- 2004-06-11 WO PCT/JP2004/008583 patent/WO2005002947A1/en active Application Filing
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110877634A (en) * | 2019-12-23 | 2020-03-13 | 天津市精一紧固件有限公司 | Steering shaft of motor vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2005002947A1 (en) | 2005-01-13 |
| JPWO2005002947A1 (en) | 2006-08-10 |
| EP1652748A4 (en) | 2007-07-18 |
| CN100436226C (en) | 2008-11-26 |
| US20060252559A1 (en) | 2006-11-09 |
| EP1652748A1 (en) | 2006-05-03 |
| US7404768B2 (en) | 2008-07-29 |
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Granted publication date: 20081126 Termination date: 20100611 |